WO2003064763A1

WO2003064763A1 - Method and device for reducing vibrations in rotating components

Info

Publication number: WO2003064763A1
Application number: PCT/DE2002/003958
Authority: WO
Inventors: Claus August BOLZA-SCHÜNEMANN
Original assignee: Koenig & Bauer Aktiengesellschaft
Priority date: 2002-02-01
Filing date: 2002-10-19
Publication date: 2003-08-07
Also published as: ATE462833T1; EP1584744A2; EP1584744A3; EP1609908A2; EP1584744B1; EP1609908A3; DE50205484D1; EP1483444B1; JP2005525512A; DE50214322D1; ES2339565T3; CN1599823A; DE50213182D1; US20050081728A1; US7040225B2; CN100443662C; US7017483B2; EP1483444A1; ATE419425T1; EP1609908B1

Abstract

The invention relates to a method for reducing undesirable flexural vibrations in at least one rotating component (01, 18). According to said method, an undesirable vibration is counteracted by means of at least one actuator (10, 11), by the derivation of a required sequence of signals and/or the intensity of the latter, based on the position of the angle of rotation of the rotating component. Said rotating component (01, 18) is then subjected to a force, based on the position of the angle of rotation.

Description

description

Method and device for reducing vibrations on rotating components

The invention relates to a method and a device for reducing vibrations on rotating components according to the preamble of claims 1, 5, 12, 30 or 36.

From EP 0 956 950 A1 a method and a device for the active suppression of vibrations is known, wherein compensating forces as a function of the measured forces z. B. be applied to rollers. The frequency for the application of force is constantly u. a. determined from the current speed, the phase and amplitude from measurements of path signals of a distance sensor.

EP 0 331 870 A2 discloses a device for supporting cylinders, wherein pins of a cylinder are mounted in two bearings arranged side by side in the axial direction of the cylinder. By means of pressure cylinders, the bearings can be moved individually perpendicular to the axis of rotation, for example, to compensate for a deflection.

WO 01/50035 A1 discloses a method for compensating oscillations of rotating components, wherein an actuator is arranged in the region of a lateral surface of the rotating component, and upon activation as a function of the rotational angle position of the rotating component of the oscillation with a force component in FIG counteracts axial direction.

JP 4-236819 A describes a system for reducing bending vibrations on a shaft, wherein a rotating disk connected to the shaft is acted upon by piezo elements via electromagnets in response to measured values with forces. WO 97/03832 A1 shows in its essay on the prior art various ways by which a deflection or a bending vibration of impression rollers static can be reduced. It proposes as a dynamic solution to measure occurring vibrations, and to use these measurements for the control and actuation of actuators.

DE 199 30 600 A1 discloses a method for reducing undesirable bending vibrations on a rotating component of a coating device with an actuator, wherein the actuator acts on a bearing journal.

The invention has for its object to provide a method and apparatus for reducing vibrations on rotating components.

The object is achieved by the features of claims 1, 5, 12, 30 or 36.

The achievable with the present invention consist in particular that with little effort a possibility was created to effectively reduce vibrations. The reduction of the vibration can take place actively during the current production.

The correlation of the countermeasure to be taken with the angular position of rotation is of particular advantage, as this, for example, many of the periodically recurring disorders such. B. asymmetries, surface defects, channels and other interruptions on the lateral surface, imbalance, is met.

The procedure allows a counteracting of an excitation or vibration at the moment of emergence, without first finding a negative effect and processed before any appropriate action is taken. Both the related to the rotation angle course of action and their size is maintained in a preferred embodiment.

Continuous measurement and further processing of data on vibrations or deformations can be omitted.

Especially when two or more cylinders work together - like. z. B. in printing units for the so-called. "Rubber-against-rubber pressure" - and one or more of the cylinder disturbances on their lateral surfaces or imbalances (asymmetries), the procedure already counteracts the development of vibrations and thus helps a "rocking "to avoid the entire system.

Embodiments of the invention are illustrated in the drawings and will be described in more detail below. Show it:

1 shows a first embodiment of the method and apparatus for reducing vibrations.

2 shows exemplary profiles of a dependence of a signal for an actuator on a rotational angle position of a cylinder (a: discrete, b: continuous);

3 shows a second embodiment of the method and the device;

4 shows a variant for the second embodiment;

Fig. 5 embodiments a), b) for the method and the device to a printing unit with four cylinders. A rotating member 01, z. B. a cylinder 01 or a roller 01 of a processing machine, in particular a rotary printing machine, for. B. for web-shaped Good, is between two side frames 02; 03 rotatably mounted. For this purpose, the cylinder 01 z. B. each end face in bearings 04; 06 mounted pin 07; 08 on. The cylinder 01 has z. B. a length of 1350 to 1550 mm and a diameter of z. B. 450 to 700, in particular from 500 to 600 mm. The cylinder 01 has z. Example, a ratio between length L01 and diameter D01 from 6 to 12, in particular between 7 and 11.

During rotation unwanted vibrations of the cylinder 01, in particular bending vibrations occur, which z. B. by non-circularities, asymmetries or by rolling on another rotating component - possibly also affected by an imbalance - may be caused. In particular, z. B. one or more axially extending on the lateral surface channels 09 for the attachment of elevators, not shown, or but shocks of elevator ends, during the rotation periodically occurring malfunctions 09, which excites the cylinder 01 to the unwanted vibrations. Common to the above-mentioned malfunctions 09 is that they occur for a known stationary operating situation in the same or at least similar manner and magnitude. A snapshot of the cylinder 01 z. B. at the inflection point of the oscillation is heavily oversubscribed in Fig. 1 by dashed lines.

To reduce the unwanted vibrations of the cylinder 01 at least one actuator 10; 11 assigned, by means of which the oscillation can be counteracted. The actuator 10; 11 is acted upon for this purpose with signals S whose sequence and / or their height is maintained in a function of a rotational angle position Φ of the rotating component. The angular position Φ of the cylinder 01 is z. B. either from a machine control, not shown, or by a not shown, the cylinder 01 driving angle-controlled electric motor, or it will determined by means of a sensor on the cylinder 01.

Fig. 2 shows exemplary representations for the course and the height of z. B. stored in a control or storage device 12 (or in a circuit) or stored signals S as a function of the angular position Φ. The illustrated, and periodically repeating period length can be in the presence of a single fault 09, for example, one revolution (2π or 360 °) in the circumferential direction, or at several symmetrically arranged comparable interference 09 z. B. an integer part of the revolution (eg., 180 °, 120 °, etc.). During a stationary operating situation, the actuator is acted upon periodically recurring with the stored sequence or height of the signal S. The dependence S (Φ) can be stored as discrete pulses (a) or as function (b) running continuously within a period. It is advantageous if an application is made with a variable force by at least one pin 04; 06 of the rotating member 01; At least 18. once per revolution targeted with a corresponding force pulse is applied. The signal S is directly correlated with the angular position Φ. For different operating situations, such. As different speed ranges, different lifts or other characteristics determining variables, various dependencies can be deposited. For example, in the vicinity of rotational speeds of the resonance frequency of the excitation of the cylinder 01 higher levels may be required than in other areas. These dependencies can also be mathematically connected to each other or generated in other ways. Thus, for nearly the same configurations, the course may be the same, but the absolute height may be correlated with the present angular velocity dΦ / dt, as offset or spread.

In the embodiment according to FIG. 1, an actuator 10 acts in each case; 11 on each one of the pin 07; 08, by a coupling 13; 14 z. B. the pin 07; 08 via a bearing 16; 17 includes. In an advantageous embodiment, the coupling 13 engages; 14 on a part of the pin, which on the side facing away from the cylinder 01 of the bearing 04; 06 about this protrudes. About the controller 12 is now the dashed line shown the cylinder 01 and pin 07; 08 counteracted, in the corresponding rotational angle positions Φ corresponding signals S, or continuously with a steady course, the actuator 10; 11 applies a counterforce (positive or negative) on the pin. The signal includes the height and, if necessary, the direction of the counterforce to be applied by the actuator. The bearings 04; 06 provide for the pin 07; 08 a clamping point. About the lever arm representing a part of the pin 07; 08, a bending moment is introduced into the cylinder 01. Although it can in principle be an actuator 10; 11 be sufficient for the cylinder 01, but advantageous is the arrangement of two actuators 10; 11, each in the region of a pin 04; 06th

The actuator 10; 11 may in particular as a piezoelectric element 10; 11 executed. The signal S controls, for example, the voltage from a voltage source, not shown, which on the piezoelectric element 10; 11 has to lie. Instead of the signal S, the actuator can also be fed directly with a corresponding voltage, which in this case is already provided by the control device 12. As actuators 10; 11 However, other facilities, such. B. magnetic force based or hydraulic units in question.

Per revolution of the cylinder 01 is or be the pin 07; 08 of the cylinder 01 at least once specifically acted upon by an external force or a force pulse or experienced at least once per revolution, a change in the externally applied force.

The cylinder 01, z. B. as a forme cylinder 01, z. B. with a second rotating member 18, for example, a second cylinder 18 such. B. a transfer cylinder 18, together, which may also have one or more axially extending interference 19 on its lateral surface. However, it can also be executed without interference 19. The control of the actuators 10; 11 is done now For example, in the above-mentioned manner such that in particular the excitation of the oscillation during the passage of the disturbances 09; 19 is steamed. When passing z. B. at the same time a corresponding pulse on the signal S on the pin 07; 08 will be given. A great advantage of this procedure is that the signal S or the opposing force is held, and therefore at the time of the excitation of a potential vibration, the counterforce or a travel is already acted upon. It is not measured until a negative impact to initiate a suitable response.

The cylinders 01; 18 are z. B. for on or off or for varying the employment in all examples, preferably with respect. Their axes of rotation at a distance from each other changeably mounted. For this purpose, at least one of the cylinders, z. B. the cylinder 01 z. B. in the eccentric 04; 06 executed bearings 04; 06 stored. However, it can also be performed pivotally on levers or in a linear guide.

In a second embodiment (FIG. 3), the cylinder 01 is movably mounted. The actuator 10; 11 attacks z. B. at the camp 04; 06 itself, which either in the side frame 02; 03 movable, or, for example, as an eccentric bearing (eg., Three- or four-ring bearing) is executed. By the actuator 10; 11, the cylinder 01 is displaceable in a direction of movement corresponding to the signals S, which is substantially perpendicular to the axis of rotation of the cylinder 01. The movement has at least one component towards or away from a cooperating cylinder 18. The cylinder 01, z. B. as a forme cylinder 01, z. B. together again with the second cylinder 18, which has no, one or more disturbances 19 on its lateral surface. The control of the actuators 10; 11 is as already set forth for the first embodiment. Here, the signal S may contain information about the travel. An excitation during the passage of the disturbance and / or a "ringing" of the cylinder 01 can be effectively reduced, depending on the deposited course of the signal S. In an embodiment variant (FIG. 4), the actuator 10 acts; 11 not directly on the cylinder 01 and its pin 07; 08, but on a pressure-on position limiting stop 21, which depending on the state of the actuator 10; 11 allows the movement of the cylinder 01 within the limits of the predetermined by the signal S travel. The counter-stop 22 is usually in pressure-on position z. B. by means of a bearing 04; 06 twisting actuator with a force F, z. B. by means of a pressure cylinder, not shown, to the stop 21. Thus, for example, when the fault 09 passes; 19 a relief by extending the stop 21 against the done, and so the excitation of the vibration are damped or suppressed. In the example, the stopper 21 is indeed in connection with an eccentric 04; 06, the procedure is, however, to be transmitted in the same way to linear bearings or bearings in pivoting levers.

Of great advantage, as shown in Fig. 5, the use of the described procedure in printing units, wherein two pairs, each a forme cylinder 01 and a transfer cylinder 01 a double pressure point for a guided between the transfer cylinders 18 and to be processed web 23, z. B. to be printed substrate web 23, form. The cylinders 01; For example, all have a circumference which is substantially the length of a printed page, z. B. newspaper page corresponds. The length L01 of the bales corresponds to z. B. substantially four times the width of four juxtaposed printed pages, z. B. Newspaper widths. In this case, the cylinders 01 and / or 18 each have a channel 09 and / or 19 in the circumferential direction. The dimensions of the cylinder 01; However, 18 may also be such that in the circumferential direction substantially two longitudinal sides, and in the longitudinal direction six or even eight side widths of a pressure side, z. B. newspaper page, can be arranged. In this case, for example, two channels 09 and / or 19 may be arranged on the circumference of the cylinder 01 and / or 18. As shown in Fig. 5 a), the equipment and the corresponding procedure for one of the transfer cylinder 18 is already conceivable to effectively reduce the vibrations in the region of the pressure point. It is achieved that at least the suggestions in the immediate vicinity of the web to be printed 23 are reduced. The phase of the disturbances 09; 19 is arranged such that the adjacent disturbances 09; 19 each roll on each other.

In Fig. 5, a) an advantageous variant is shown by dashed lines, wherein a forme cylinder 01 and a transfer cylinder 18 are operated in the appropriate procedure. The version with actuator 10; 11 is preferably on non-moving cylinders 01; 18 arranged.

If such disturbances 19 are present only on the forme cylinders 18, or if it is intended to reduce the oscillations at the nip point between mold 01 and transfer cylinder 18 in the main, then it is advantageous to carry out only the two forme cylinders 18 with the described device and operate in the envisaged procedure (FIG. 5 b)). In this case, if necessary, the opposing force can be increased on the forme cylinder 01, in order to achieve parallel oscillation of the two cooperating cylinders 01; 18 to reach.

Advantageously, the arrangement of cylinders 01; 18, which does not have to be moved to the on and off. However, it is also possible, for example, only the two transfer cylinders 18, or all cylinder 01; 18 to perform with the device.

The solutions illustrated by means of a rubber-to-rubber printing unit are of course also applicable to printing units having a satellite cylinder, such as. B. nine-cylinder or ten-cylinder printing units. The procedure is also applicable to other processing machines in which materials are to be transported and / or processed as accurately as possible by means of rotating components. In particular, the procedure and the device is advantageous if the rotating component 01 on its lateral surface a fault 09; 19, an imbalance due to manufacturing or asymmetries, and / or cooperates with a second rotary body 18 having one of the said properties.

The procedure for the entire method is as follows: First, a course of the undesirable oscillation as a function of the rotational angle position Φ is determined for a specific configuration and / or mode of operation. This can be done by an additional, but not shown sensor. In an advantageous embodiment, the actuator 10; 11 at the same time as a sensor use, such as the z. B. in the case of a piezoelectric element 10; 11 is possible.

Subsequently, empirically and / or by theoretical derivation with the aid of this dependence, a course of a suitable opposing force or a travel that is dependent on the angular position Φ is determined in such a way that the excitation itself and / or the oscillation is effectively suppressed. For this mode of operation, the progression of the oscillation itself and / or the profile of the determined opposing force or travel is stored in the memory unit 12. The course for the application is thus predetermined and during operation largely independent of the vibration characterizing measured values, but ultimately only of the angular position Φ.

The determined course or the height can now also be used for other modes of operation or configurations, if the tolerances in the finished product, the machine load, etc. allow this. The rotating component is periodically recurring during these comparable stationary operating situations obtained and stored signals according to the course of the determined counterforce or the travel acted upon.

In the other case, the described process is carried out for various practical operating modes / configurations, and the corresponding dependency S (Φ) is stored together with the parameters characterizing the operating mode / configuration. These dependencies S (Φ) can each be retrieved for the desired production and used in the manner described to reduce the vibrations.

For the procedure during production, therefore, no constant determination of current variables for characterizing the oscillation is absolutely necessary. The procedure works quickly and effectively, since the action to be taken is already held before the occurrence of the event (disturbance, oscillation).

In an embodiment different from the mentioned embodiment, however, the required amplitude and / or the phase (or the time) for the application of the signal S (for the force to be applied or the force pulse or the time sequence) in dependence on a from the angular position Φ different measured variable, for. B. a current displacement or force measurement on the cylinder 01 or its pin 04; 06, done. It may also be a mixed form of the method be advantageous, although a basic pattern and a base force based on held, z. B. angle position dependent, given data, however, an adjustment of height and time based on other determined measurements is made. A system which is based on stored signals S or sequences can also be designed to be self-learning and / or adaptive. In this case, the system uses on the one hand the reliable and rapid method of "controlling", before a measurement of the error and only then a reaction takes place, improvements of the algorithm or of the held signals S or sequences and / or heights However, for example, the oscillation via a measurement is continuous or specific Determines cycles, and the stored parameters for the signals S changed or supplemented.

In an advantageous, because simple design is ever on the cylinder 01; 18 circumferentially arranged channel per revolution only an external excitation, d. H. a signal S or a force pulse (eg pulse, ramp, triangle or delta-shaped) the cylinder 01; 18 and the pin 04; 06 imprinted. The oscillation excited by this one force pulse (per channel and per revolution) forms a negative interference to the channel 09; 19 or an interrupt 09; 19 excited vibration when the relative angular position Φ between channel excitation and external force pulse suitably selected and the amplitude is corresponding.

As on the cylinder 01; 18 a line load is applied by the pressing of the blankets under which the cylinder 01; Bend 18 are in an advantageous embodiment by the additional bearing 16; 17, the support bearings 16; 17, sitting outside of the bearings 04, introduced forces that initiate a reverse bend and thus reduce the entire deflection. Since the line load at the moment of Kanalüberrollung temporarily omitted (or at least reduced), the force that the outer bearing 16 on the pin 07; 08 bring in this time window also omitted (or be withdrawn), otherwise overshoot of the cylinder 01; 18 would be the result. By the controlled introduction of the bending forces on the pin 07; During the channel rollover, the cause of the swing, the channel impact (ie the elimination of the bending moment exerted by the blanket), can be partially compensated. The force control must be carried out in an advantageous embodiment in a time window which corresponds approximately to the duration of Kanalüberrollung. An alternative to this would be, as already mentioned in Fig. 2b), the application of "countervibrations" to the vibrations of the cylinder 01, 18. (control of symptoms) However, an advantage with this variant is that the force control is not so must be highly dynamic, since the relevant time window then by the oscillation frequency of the cylinder 01, 18 and not by the short time of the rollover given is.

Especially for cylinder 01; 18, the ratio between length L01 and diameter D01 from 6 to 12, in particular 7 to 11 is the embodiment of advantage, wherein in the axial direction of the pin 07; 08 a distance a from the center of the bearing 04; 06 to middle camp 16; 17 is about 100 to 230 mm. For diameters (at least in the region of the point of application of the bearings 16, 17) of the pin 07; 08 from 55 to 65 mm, the distance is preferably 125 to 175 mm, while for diameters of 65 to 75 mm z. B. is 150 to 230 mm. The pin 07; 08 is during the pulse with a maximum force of z. B. 5 to 15 kN, in particular 7.5 to 11 kN acted upon. A movement of the support bearing 16; 17 is advantageously 25 to 100 microns, for diameters of 55 to 65 mm z. B. at 45 to 100 microns, especially at about 60 microns, and for diameters of 65 to 75 mm z. B. at 25 to 80 microns.

The introduction of this force can now be done in two different variants: Thus, the force during the duration of rotation without interference (no rollover) applied continuously, and thus the opposite bending be generated. This can be done via the actuator itself in a "positive" direction, or via a corresponding mechanical bias.This force is then briefly withdrawn or switched off in the time window of the overrun, which in the first case by withdrawal at the actuator itself and in the second case by counteracting As a result, the static bending is also reduced.

At a rotational speed of 20,000 U / h (revolutions per hour) is the time window for the application or redemption z. B. at 1, 5 to 5.0 ms, especially at 2.5 to 4.0 ms. At 90,000 U / h. the time window at 0.3 to 1.0 ms, in particular at 0.6 to 0.8 ms. These time windows are associated with widths of the channel opening on the lateral surface in the circumferential direction of 1 to 3 mm. For openings twice as wide, the time windows are about a factor of two, for openings four times as wide Factor four larger.

In an advantageous embodiment, the actuator 10; 11 together with control or storage device 12 and power supply designed such that a force of z. B. 7.5 to 11 kN at a distance z. B. at 25 to 100 microns, can be applied. For this purpose, preference is given to a piezoelectric system, wherein the actuator 10; 11 as above as a piezoelectric element 10; 11 is executed.

LIST OF REFERENCE NUMBERS

01 rotating component, cylinder, forme cylinder

02 side frame

03 side frame

04 bearings

05 -

06 bearings

07 cones

08 cones

09 Fault, channel, interruption

10 actuator, piezo element

11 actuator, piezo element

12 control device

13 paddock

14 paddock

15 -

16 bearings

17 bearings

18 rotating component, cylinder, transfer cylinder

19 fault, channel

20 -

21 stop

22 counter-attack

23 web, substrate web

a distance (04, 16, 06, 18)

D01 Diameter (01) L01 Length (01) F force

S signal

Φ angular position dΦ / dt angular velocity

Claims

Expectations

1. A method for reducing undesirable bending vibrations on at least one rotating component (01; 18) with at least one actuator (10; 11) which can be acted upon by signals (S), by means of which an undesired vibration is counteracted, characterized in that a required sequence of Signals (S) and / or their height are provided as a function of the rotational angle position (Φ) of the rotating component, and the rotating component is acted upon as a function of the rotational angle position (Φ).

2. The method according to claim 1, characterized in that the signal (S) includes the height and the direction of a counterforce to be applied or changed by the actuator (10; 11).

3. The method according to claim 1, characterized in that the signal (S) includes the size and direction of a required travel.

4. The method according to claim 1, characterized in that during a stationary operating situation, the actuator (10; 11) is periodically subjected to the sequence or height provided.

5. A method for reducing undesirable bending vibrations on at least one rotating component, a course of the undesired vibration depending on the angle of rotation (Φ) first being determined and, with the aid of this dependence, a course of a counterforce to be impressed or changed that is dependent on the angle of rotation (Φ) , the course of the vibration and / or the determined counterforce being stored and held in a control and / or storage device (12), and the rotating component (01;

18) periodically recurring during a stationary operating situation Signals (S) is applied according to the course of the determined and held counterforce.

6. The method according to claim 5, characterized in that the rotating component (01; 18) via at least one actuator (10; 11) is acted upon by the counterforce or a change in the counterforce.

7. The method according to claim 4 or 6, characterized in that the application of the actuator (10; 11) during, the production without the imperative of a constant determination of current quantities. to characterize the vibration.

8. The method according to claim 1 or 6, characterized in that the actuator (10; 11) acts at least indirectly on a in a side frame (02; 03) mounted pin (07; 08) of the rotating component (01; 18). ^•

9. The method according to claim 1 or 8, characterized in that by means of the actuator (10; 11), depending on its state, a position and / or shape of an axial bending line of at least the pin (07; 08) is changed.

10. The method according to claim 1 or 8, characterized in that the actuator (10; 11) acts on a part of the pin (07; 08) lying on the side of the bearing (04; 06) facing away from the rotating component (01; 18), and that the bearing (04; 06) acts as a clamping point for bending or lever loading.

11. The method according to claim 1 or 8, characterized in that the actuator (10; 11) changes the position of the pin (07; 08) within a plane perpendicular to the axis of rotation of the rotating component (01; 18) depending on its state.

12. A method for reducing undesired bending vibrations on at least one rotating component (01, 18) rotatably mounted in bearings (04; 06) with pins (07; 08) at both ends, characterized in that by means of at least one on at least one of the pins (07; 08) acting actuator (10; 11) a shape of an axial bending line of at least the pin (07; 08) is changed by the actuator (10; 11) with one of an angular position (Φ) of the cylinder (01; 18 ) dependent signal (S) for generating or changing a counterforce.

13. The method according to claim 12, characterized in that the actuator (10; 11) acts with at least one component in the radial direction on the pin (07; 08).

14. The method according to claim 10 or 12, characterized in that the actuator (10; 11) at least indirectly on the pin (07; 08) at a distance (a) to the center of the bearing (04; 06) of 100 to 230 mm works. :

15. The method according to claim 10 or 12, characterized in that the actuator (10; 11) acts on a bearing (16; 17) receiving the pin (07; 08), the center of which in the axial direction is a distance (a) from the center of the bearing (04; 06) from 100 to 230 mm.

16. The method according to claim 14 or 15, characterized in that the actuator (10; 11) with a diameter of the pin (07; 08) from 55 to 65 mm at a distance (a) of 125 to 175 mm on the pin (07; 08) works.

17. The method according to claim 14 or 15, characterized in that the actuator (10; 11) with a diameter of the pin (07; 08) of 65 to 75 mm at a distance (a) of 150 to 230 mm on the pin (07; 08) works.

18. The method according to claim 12, characterized in that the actuator (10; 11) acts on a part of the pin (07; 08) lying on the side of the bearing (04; 06) facing away from the rotating component (01; 18)

19. The method according to claim 12, characterized in that the signal (S) is applied to the actuator (10; 11) periodically. .

20. The method according to claim 12, characterized in that a course of the signal (S) dependent on the angle of rotation position (Φ) is provided.

21. The method according to claim 4, 5 or 14, characterized in that the period length corresponds to a full revolution of the rotating component (01; 18) or a quotient of one revolution and an integer.

22. The method according to claim 2, 5 or 12, characterized in that the counterforce or its change are applied as a discrete pulse or a plurality of discrete pulses.

23. The method according to claim 2, 5 or 12, characterized in that the counterforce or its change is applied as a function which runs continuously within a period.

24. The method according to claim 2, 5 or 12, characterized in that the change in the counterforce by means of the signal (S) relieves an existing bias.

25. The method according to claim 2, 3, 5 or 12, characterized in that the counterforce and / or the displacement is directly correlated with the angle of rotation position (Φ).

26. The method according to claim 4 or 20, characterized in that the dependency held is determined by first determining a course of the undesired vibration as a function of the angle of rotation (Φ) of the rotating component (01; 18), that with the aid of this dependency a curve for the counterforce dependent on the angle of rotation position (Φ) is determined, and the curve of the vibration and / or the counterforce determined is stored in a control and / or storage device.

27. The method according to claim 5 or 26, characterized in that the undesired course of the vibration is determined with at least one sensor.

28. The method according to claim 26, characterized in that the actuator (10; 11) is used as a sensor and vice versa.

29. The method according to claim 1, 6, 12 or 27, characterized in that a piezo element (10; 11) is used as the actuator (10; 11) or sensor.

30. A method for reducing undesirable vibrations on at least one rotating component (01; 18), an undesirable vibration being counteracted by applying a variable force, characterized in that at least one pin (04; 06) of the rotating component (01 ; 18) a force impulse is applied at least once per revolution or a preload is relieved in a targeted manner.

31. The method according to claim 30, characterized in that the pin (07; 08) is acted upon by an externally impressed force pulse or relief in addition to the forces caused by the oscillation or the oscillation-induced impulses.

32. The method according to claim 30, characterized in that depending on the rotating component (01; 18) arranged in the circumferential direction disturbance (09; 19) per revolution only one external stimulus, in particular in the form of a force pulse or a relief, is impressed.

33. The method according to claim 31 or 32, characterized in that the shape and / or duration of the impressed force pulse or the relief of an excitation is modeled, which is caused by the rolling of a disturbance arranged on the circumference of the cylinder (01; 18) (09 ; 19) on a second cylinder (18; 01).

34. The method according to claim 30, characterized in that the force pulse or the relief of the pin (04; 06) on a side facing away from the cylinder (01; 18) of a bearing (04; 06) receiving the pin (04; 06) is imprinted.

35. Device for performing the method according to claim 1, 5, 12 or 30, characterized in that the rotating component (01; 18) is designed as a cylinder (01) of a printing press.

36. Device for reducing undesirable bending vibrations on at least one rotating component (01; 18) rotatably mounted in both bearings (04; 06) with pins (07; 08) with at least one actuator (10; 11), by means of which one undesired vibration is counteracted, the actuator (10; 11) acting on a part of the pin (07; 08) lying away from the rotating component (01; 18) of the journal (04; 06), characterized in that the actuator ( 10; 11) acts on a bearing (16; 17) receiving the pin (07; 08), the center of which in the axial direction is at a distance (a) from the center of the bearing (04; 06) of 100 to 230 mm.

37. Device according to claim 35 or 36, characterized in that the pin (07; 08) via the bearing (16; 17) is periodically acted upon by a force pulse of at most 5 to 15 kN.

38. Device according to claim 35 or 36, characterized in that the pin (07; 08) via the bearing (16; 17) is subjected to a preload of 5 to 15 kN and is periodically relieved.

39. Device according to claim 35 or 36, characterized in that the rotating component (01; 18) has a ratio between a length (L01) and a diameter (D01) of its bale, which is between 11 and 7.

40. Device according to claim 36, characterized in that the rotating component (01; 18) is designed as a cylinder (01) of a printing press.

41. Device according to claim 35 or 36, characterized in that the component (01; 18) designed as a cylinder (01) of a printing press works together in a printing position with at least one second cylinder (18) as the first pair.

42. Device according to claim 41, characterized in that only one of the two cylinders (01; 18) has an actuator (10; 11) to which the signal (S) can be applied.

43. Device according to claim 41, characterized in that two pairs with a total of four cylinders (01; 18) form a double pressure point between the inner cylinders (18), and that only the two outer cylinders (01) one with a signal ( S) have an actuatable actuator (10; 11).

44. Apparatus according to claim 41, characterized in that two pairs with a total of four cylinders (01; 18) form a double pressure point between the inner cylinders (18), and that only the two cylinders (18) forming the pressure point, each with a signal (S) actable actuator (10; 11).

45. Device according to claim 41, characterized in that two pairs with a total of four cylinders (01; 18) form a double pressure point between the inner cylinders (18), and that an inner and an outer cylinder (01; 18) each have one has a signal (S) to which an actuator (10; 11) can be applied.

46. Device according to claim 41, characterized in that two pairs with a total of four cylinders (01; 18) form a double pressure point between the inner cylinders (01), and that only one of the two cylinders (01) forming the pressure point forms one with one each Signal (S) actable actuator (10; 11).

47. Device according to claim 41, characterized in that two pairs with a total of four cylinders (01; 18) form a double pressure point between the inner cylinders (18), and that all four cylinders (01; 18) each have a signal (S ) actable actuator (10; 11).